Compressor and compression system

Abstract

The invention belongs to the technical field of compressors, and provides a compressor and a compression system.The compressor comprises a shell, a compression cavity for installing a female rotor and a male rotor is formed in the shell, and the compression cavity sequentially comprises an air suction section, a low-pressure compression cavity section and a high-pressure compression cavity section in the axial direction of the rotors; the shell is provided with a plurality of spray holes, and the spray holes are all located in the low-pressure compression cavity section and used for spraying cooling media into the compression cavity. The arrangement positions of the spraying holes are optimized, and the spraying holes are all designed in the low-pressure compression cavity section of the compression cavity; as the low-pressure compression cavity section is located at the closed section of the compression cavity, the air suction volume flow of the compressor can be guaranteed, and it is guaranteed that the environment pressure in the air suction process of each inter-tooth air suction volume is not affected by a spray hole; meanwhile, the pressure of the low-pressure compression cavity section is low, the driving power load of a pump for spraying the cooling medium is minimum, the driving power of the compressor is reduced, and energy conservation and high efficiency are achieved.

Description

Technical Field

[0001] This application relates to the technical field of compressors, and particularly to a compressor and a compression system. Background Art

[0002] Screw compressors are compression devices widely used in industrial fields. Their working principle is that through the meshing of male and female rotors, a compression chamber is formed within the housing, and gas is transported from the low-pressure area to the high-pressure area and the compression process is completed. During the compression process, the gas temperature will increase significantly. Therefore, effective cooling measures need to be taken to ensure the normal operation of the compressor and improve efficiency.

[0003] In related technologies, heat exchange is achieved by spraying water or oil through a single hole or multiple holes on the compressor housing to achieve temperature control. However, the hole positions are designed in the suction section or the high-pressure sealed chamber section of the compression chamber. When the hole positions are designed in the suction section, this design seriously affects the suction volume flow rate. When the hole positions are designed in the high-pressure sealed chamber section of the compression chamber, the driving shaft power of the main unit is increased, and the energy consumption increases. Summary of the Invention

[0004] The purpose of this application is to provide a compressor and a compression system, which can improve the above problems.

[0005] One aspect of the present invention provides a compressor, which includes a housing. A compression chamber for installing a male rotor and a female rotor is formed within the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes are provided on the housing, and all of the plurality of spray holes are located in the low-pressure compression chamber section for spraying a cooling medium into the compression chamber.

[0006] In some embodiments of this application, the plurality of spray holes are distributed in a spiral.

[0007] In some embodiments of this application, the plurality of spray holes include a plurality of first spray holes, and the plurality of first spray holes are distributed in a first spiral. The lead of the first spiral is equal to the lead of the outer diameter of the male rotor tooth tip, and the spiral angle of the first spiral is equal to the spiral angle of the male rotor.

[0008] In some embodiments of this application, the plurality of spray holes include a plurality of second spray holes, and the plurality of second spray holes are distributed in a second spiral. The lead of the second spiral is equal to the lead of the outer diameter of the female rotor tooth tip, and the spiral angle of the second spiral is equal to the spiral angle of the female rotor.

[0009] In some embodiments of this application, the spray holes are atomizing spray holes for spraying a mist-like cooling medium into the compression chamber.

[0010] In some embodiments of the present application, the diameter range of the atomizing nozzles is 0.1 mm - 2 mm.

[0011] In some embodiments of the present application, the starting angle of the first spiral is determined by the following formula: ; The starting angle of the second spiral is determined by the following formula: ; In the formula: is the starting angle of the first spiral, is the starting angle of the second spiral, is the intake angle of the male rotor, is the intake angle of the female rotor, is the number of teeth of the male rotor, is the number of teeth of the female rotor, is the tip radius of the male rotor tooth, is the tip radius of the female rotor tooth, is the diameter of the first nozzle hole, is the diameter of the second nozzle hole.

[0012] In some embodiments of the present application, the number of the nozzle holes on the housing satisfies: ; wherein, is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the nozzle hole.

[0013] In some embodiments of the present application, the plurality of nozzle holes are distributed at intervals along the axial direction of the housing.

[0014] The second aspect of the present application further provides a compression system, which includes the compressor described above.

[0015] The twin-screw compressor includes a housing, and a compression chamber for installing a female rotor and a male rotor is formed in the housing. The compression chamber sequentially includes an intake section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. Nozzle holes for spraying a cooling medium into the compression chamber are provided on the housing. Different from the prior art in which the nozzle holes are arranged in the intake section or the high-pressure compression chamber section of the compression chamber, the present application optimizes the arrangement position of the nozzle holes and designs the nozzle holes in the low-pressure compression chamber section of the compression chamber; since the low-pressure compression chamber section is in the closed section of the compression chamber, the suction volume flow rate of the compressor can be guaranteed, and the ambient pressure of the suction process of each tooth space suction volume is not affected by the nozzle holes; at the same time, the pressure in the low-pressure compression chamber section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, which is energy-saving and efficient. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] To more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the drawings required for the description of the embodiments of the present invention or the prior art. Obviously, the following described drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0017] Figure 1 is a schematic structural diagram of a compressor shown in some embodiments of the present invention; Figure 2 is Figure 1 a cross-sectional view of the compressor shown in Figure 3 is Figure 1 a schematic structural diagram of the housing of the compressor shown in Figure 4 is Figure 3 another schematic structural diagram of the housing of the compressor shown in Figure 5 is Figure 3 yet another schematic structural diagram of the housing of the compressor shown in Detailed implementation manners

[0018] The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the drawings in the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present invention.

[0019] The terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more.

[0020] In the description of this specification, specific features, structures, materials, or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0021] A twin-screw compressor is a rotary positive-displacement compressor. Its core components are a pair of meshing male and female rotors. Through the meshing of the male and female rotors, a compression chamber is formed in the housing to transport the gas from the low-pressure area to the high-pressure area and complete the compression process. During the compression process, the gas temperature will increase significantly. Therefore, effective cooling measures need to be taken to ensure the normal operation of the compressor and improve efficiency.

[0022] For the gas overheating phenomenon generated during the operation of a twin-screw compressor, in related technologies, single holes with a linear distribution of male and female rotors or multiple holes with a linear distribution are used to spray water or oil for heat exchange to achieve the purpose of temperature control; for larger flow rates and higher flow rates, the hole diameter is increased or the number of holes with a linear distribution is increased to achieve temperature control. In some designs, the holes are designed in the suction process section, seriously affecting the suction volumetric flow rate; for the multi-hole structure, problems such as unbalanced spray hole pressure, different flow rates and flow velocities, and backflow from the high-pressure chamber to the low-pressure chamber occur; and for the design of holes in the high-pressure closed chamber section, the driving shaft power of the main unit is increased; the energy consumption increases.

[0023] In view of this, to solve the above problems, in combination with Figures 1 to 5 As shown, in some embodiments of the present application, a compressor is proposed. The compressor includes a housing 1. A compression chamber for installing a male rotor 21 and a female rotor 22 is formed inside the housing 1. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes 3 are provided on the housing 1. The plurality of spray holes 3 are located in the low-pressure compression chamber section and are used to spray a cooling medium into the compression chamber.

[0024] Specifically, the compressor housing 1 is made of cast iron or steel material, having sufficient strength and stiffness to withstand the pressure and temperature generated during the compression process. The inside of the housing 1 is designed with a precision-machined compression chamber for installing the male rotor 21 and the female rotor 22. The male rotor 21 and the female rotor 22 are respectively supported at both ends of the housing 1 by bearings and maintain an accurate relative position relationship through synchronous gears. The tooth profiles of the male rotor 21 and the female rotor 22 are designed as involute curves to ensure the formation of a continuously changing sealed chamber during rotation.

[0025] The compression chamber is divided into three functional regions along the axial direction of the rotor: a suction section, a low-pressure compression chamber section, and a high-pressure compression chamber section. The suction section is located at one end of the compression chamber and is provided with a suction port for sucking the gas to be compressed; the low-pressure compression chamber section is located in the middle position where the gas begins to be compressed and the pressure gradually increases but has not reached the maximum value; the high-pressure compression chamber section is located at the other end of the compression chamber where the gas is compressed to the highest pressure and discharged through the exhaust port.

[0026] On the housing 1, particularly at positions corresponding to the low-pressure compression chamber section, a plurality of spray holes 3 are provided. These spray holes 3 are connected to an external cooling medium supply system for injecting a cooling medium into the compression chamber. The cooling medium can be lubricating oil, water, or other suitable liquids, and is pressurized by an external pump system and then fed into the spray holes 3. The positions of the spray holes 3 precisely correspond to the low-pressure compression chamber section. Since the low-pressure compression chamber section is in the sealed section of the compression chamber, this can ensure the suction volume flow rate of the compressor and ensure that the ambient pressure during the suction process of each inter-tooth suction volume is not affected by the spray holes 3. At the same time, the pressure in the low-pressure compression chamber section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, which is energy-saving and efficient.

[0027] In some embodiments of the present application, the plurality of spray holes 3 are distributed in a spiral. This distribution method enables the cooling medium to be evenly sprayed along the rotation direction of the rotor, ensuring that all parts in the compression chamber can be sufficiently cooled. The spray holes 3 distributed in a spiral can also continuously inject the cooling medium into the compression chamber as the rotor rotates, avoiding the problem of uneven cooling. At the same time, the design of the multi-spray holes 3 in a spiral distribution can spray-cool the entire screw rod, which can reduce the driving power consumption of the compression main shaft power.

[0028] In the related art, the plurality of spray holes 3 are distributed in a straight line, which may cause some spray holes 3 to be distributed in the suction section, some spray holes 3 to be distributed in the low-pressure compression chamber section, and some spray holes 3 to be distributed in the high-pressure compression chamber section, resulting in an unbalanced pressure at the water spraying points of the hole positions; there is also a risk that the gas in the high-pressure chamber may flow back to the low-pressure chamber, affecting the performance. In some embodiments of the present application, the plurality of spray holes 3 include a plurality of first spray holes 31, and the plurality of first spray holes 31 are distributed in a first spiral L1. The lead of the first spiral L1 is equal to the lead of the outer diameter of the tooth tip of the male rotor 21, and the spiral angle of the first spiral L1 is equal to the spiral angle of the male rotor 21. This design can not only make the distribution of the first spray holes 31 completely match the rotation trajectory of the male rotor 21, ensuring that the cooling medium can be precisely injected into the compression chamber formed between the tooth tip of the male rotor 21 and the inner wall of the housing 1, improving the cooling efficiency. At the same time, since each first spray hole 31 corresponds to the same inter-tooth groove, the pressure received by each first spray hole 31 is equal, and thus the flow rate and flow velocity of each first spray hole 31 can be equal, avoiding the backflow phenomenon caused by the unbalanced pressure of each first spray hole, and improving the safety of the compressor.

[0029] Furthermore, in some embodiments of the present application, the plurality of spray holes 3 includes a plurality of second spray holes 32, the plurality of second spray holes 32 are distributed in a second spiral line L2, the lead of the second spiral line L2 is equal to the lead of the outer diameter of the tooth tip of the female rotor 22, and the spiral angle of the second spiral line L2 is equal to the spiral angle of the female rotor 22. This can not only be designed such that the distribution of the second spray holes 32 completely matches the rotation trajectory of the female rotor 22, ensuring that the cooling medium can be accurately sprayed into the compression cavity formed between the tooth tip of the female rotor 22 and the inner wall of the housing 1, further improving the overall cooling efficiency of the machine. At the same time, each second spray hole 32 faces the same tooth space, so that the pressure received by each second spray hole 32 is equal. Furthermore, the flow rate and flow velocity of each second spray hole 32 can be equal, avoiding the backflow phenomenon caused by the pressure imbalance of each second spray hole 32 and improving the safety of the compressor.

[0030] In some embodiments of the present application, the first spray holes 31 and the second spray holes 32 are simultaneously provided on the housing 1. The first spray holes 31 are located on the housing 1 that matches the position of the male rotor 21, and the second spray holes 32 are located on the housing 1 that matches the position of the female rotor 22. The first spray holes 31 are distributed along the first spiral line L1 on the housing 1, and the second spray holes 32 are distributed along the second spiral line L2; in the low-pressure compression cavity section, each spray hole 3 communicates with the corresponding tooth space, and the pressure received by each spray hole 3 is consistent, so as to ensure that the flow rate and flow of each spray hole 3 are consistent, avoiding the backflow problem caused by the inconsistent pressure of each spray hole 3.

[0031] Of course, it can be understood that the above-mentioned plurality of first spray holes 31 can also be provided only on the housing 1 that matches the position of the male rotor 21, or the above-mentioned plurality of second spray holes 32 can also be provided only on the housing 1 that matches the position of the female rotor 22, which is not limited here.

[0032] In the related art, for large-flow models, the heat dissipation efficiency is often improved by increasing the aperture, but this will cause the cooling medium in the compression cavity to exist in a relatively large liquid form. The liquid cannot be compressed, occupying the volume of the compression cavity, and is prone to the risk of liquid hammer.

[0033] In some embodiments of the present application, the spray holes 3 are atomizing spray holes for spraying a mist-like cooling medium into the compression cavity. The atomizing spray holes adopt a special structural design inside, so that the cooling medium is atomized into fine droplets when passing through the spray holes 3. This mist-like cooling medium has a larger specific surface area, can absorb the heat generated during the compression process more quickly, and improve the cooling efficiency. At the same time, the mist-like cooling medium is more evenly distributed, can cover a larger area in the compression cavity, and avoid local overheating.

[0034] In some embodiments of the present application, the diameter of the atomizing nozzle hole 3 ranges from 0.1 mm to 2 mm. Optionally, the diameter of the atomizing nozzle hole 3 is 0.1 mm, 0.2 mm, 0.3 mm, 0.4 mm, 0.5 mm, 0.6 mm, 0.7 mm, 0.8 mm, 0.9 mm, 1 mm, 1.1 mm, 1.2 mm, 1.3 mm, 1.4 mm, 1.5 mm, 1.6 mm, 1.7 mm, 1.8 mm, 1.9 mm, 2 mm, etc. When the diameter of the nozzle hole 3 is 0.1 mm, the cooling medium is atomized into extremely fine droplets, and the cooling effect is the best, but the requirement for the purity of the cooling medium is relatively high, and it is prone to blockage; when the diameter of the nozzle hole 3 is 2 mm, the atomization effect of the cooling medium is relatively poor, but the flow rate is large and it is not easy to block. In practical applications, the appropriate diameter of the nozzle hole 3 can be selected according to the type and purity of the cooling medium. For example, for a cooling medium containing a small amount of impurities, a nozzle hole 3 with a diameter of 1.5 mm can be selected, which can not only ensure a certain atomization effect but also is not easy to block.

[0035] In some embodiments of the present application, as Figure 4 shown, the center of the first nozzle hole 31 is distributed in a first spiral line L1, and the center of the second nozzle hole 32 is distributed in a second spiral line L2. The chord length angle of the diameter of the first nozzle hole 31 on the housing 1

[0036] ; The chord length angle of the diameter of the second nozzle hole 32 on the housing 1

[0037] ; In some embodiments of the present application, the suction angle of the male rotor 21 plus the tooth space angle of the male rotor 21 , plus half of the chord length angle of the diameter of the first nozzle hole 31 on the housing 1 , after arrangement, the included angle of the starting point of the first spiral line L1 formed by the center of the first nozzle hole 31 : ; That is: ; Similarly, the suction angle of the female rotor 22 plus the tooth space angle of the male rotor 21 , plus half of the chord length angle of the diameter of the second nozzle hole 32 on the housing 1 , after arrangement, the included angle of the starting point of the second spiral line L2 formed by the center of the second nozzle hole 32 is: ; That is: ; In the formula: is the starting angle of the first helical line L1, is the starting angle of the second helical line L2, is the suction angle of the male rotor 21, is the suction angle of the female rotor 22, is the number of teeth of the male rotor 21, is the number of teeth of the female rotor 22, is the tip radius of the male rotor 21, is the tip radius of the female rotor 22, is the diameter of the first injection hole 31, is the diameter of the second injection hole 32.

[0038] The helical line starting angle of the injection hole 3 calculated through these formulas can ensure that the position of the injection hole 3 is precisely matched with the rotational position of the rotor, enabling the cooling medium to be injected into the compression chamber at the optimal timing. For example, the number of teeth of the male rotor 21 is 5, and the number of teeth of the female rotor 22 is 7; according to the parameters of the male and female rotors, the suction angle of the male rotor is calculated to be 277.787°, and the suction angle of the female rotor is 233.573°, the tip radius of the male rotor 21 is 50 mm, and the tip radius of the female rotor 22 is 45 mm; the diameter of the first injection hole 31 is 1.5 mm, and the diameter of the second injection hole 32 is 1.5 mm. According to the above formulas, the starting angle of the first helical line L1 can be calculated to be 350.647°, and the starting angle of the second helical line L2 is 285.956°. Among them, the method of obtaining the suction angle of the male rotor and the suction angle of the female rotor based on the parameters of the male and female rotors is a well-known technology and will not be described in detail here.

[0039] In actual design, the cooling medium flow rate of the twin-screw compressor can be calculated first according to thermodynamics, and then the number of injection holes 3 can be obtained based on the flow rate and the hole diameter of the injection hole 3.

[0040] In some embodiments of the present application, the number of the injection holes 3 on the housing 1 satisfies: ; where is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the injection hole 3. This design ensures that the number of injection holes 3 can meet the requirements of the designed flow rate of the cooling medium. For example, when the flow rate of the cooling medium calculated according to the thermal performance of temperature control is 10 L / min and the flow velocity of the cooling medium is 8 m / s, it is calculated that the number of injection holes should be no less than 12. Of course, according to the actual design requirements, the number of injection holes can be appropriately increased or decreased to meet the cooling requirements.

[0041] In some embodiments of the present application, the multiple injection holes 3 are on the housing 1. On the one hand, they are distributed along a helix with the same lead and helix angle as the female rotor 22 and the male rotor 21. On the other hand, according to the thermal distribution during the twin-screw compression process, the multiple injection holes 3 are spaced apart along the axial direction of the housing. This distribution method ensures that the cooling medium can evenly cover the entire low-pressure compression cavity section, avoiding local overheating. The equally spaced injection holes 3 also simplify the processing technology of the housing 1, reduce the manufacturing cost. At the same time, the pressure received by each injection hole 3 is equal, so that the flow rate and flow velocity of each injection hole 3 are equal, avoiding the backflow phenomenon caused by the pressure imbalance of each injection hole 3 and improving the safety of the compressor.

[0042] In practical applications, the working process of the compressor is as follows: First, the gas enters the suction process section through the suction port; then, as the female rotor 22 and the male rotor 21 rotate, the gas is brought into the low-pressure compression cavity section to start compression; at this time, the cooling medium is sprayed into the compression cavity through the multiple injection holes 3 to absorb the heat generated during the compression process; finally, the gas enters the high-pressure compression cavity section to be further compressed to the highest pressure and is discharged through the exhaust port. During the whole process, the injection of the cooling medium effectively controls the temperature rise during the compression process, improving the efficiency and reliability of the compressor.

[0043] The second aspect of the present application also provides a compression system, which includes the aforementioned compressor. The compressor optimizes the setting position of the injection holes 3 and designs all the injection holes 3 in the low-pressure compression cavity section of the compression cavity; since the low-pressure compression cavity section is in the closed section of the compression cavity, this can ensure the suction volume flow rate of the compressor and ensure that the ambient pressure of the suction process of each inter-tooth suction volume is not affected by the injection holes 3; at the same time, the pressure in the low-pressure compression cavity section is relatively low, and the driving power load of the pump for spraying the cooling medium is minimized, reducing the driving power of the compressor, being energy-saving and efficient, and improving the working efficiency of the entire compression system.

[0044] Furthermore, multiple injection holes 3 are provided on the housing 1, and the multiple injection holes 3 present a helix hole position distribution with the same lead and the same helix direction as the female rotor and the male rotor. Each injection hole 3 faces the same tooth space between the female and male rotors, so the pressure received by each injection hole 3 position is equal, thus ensuring that the flow rate and flow velocity of each injection hole 3 are equal, and the phenomenon of gas backflow through the injection holes can be avoided.

[0045] In some embodiments of the present application, the compression system, in addition to including the above-mentioned compressor, further includes a cooling medium supply system, a drive system, and a control system. The cooling medium supply system includes a cooling medium storage tank, a filter, a pump, and pipelines, and is used to supply clean and constant-pressure cooling medium to the injection holes 3 of the compressor. The drive system includes a motor and a transmission device, and is used to drive the rotation of the male rotor of the compressor. The male rotor maintains an accurate relative position relationship with the male rotor through a synchronous gear. The control system includes various sensors, a controller, and actuators, and is used to monitor and control the operating state of the compression system.

[0046] The pump in the cooling medium supply system pumps the cooling medium out of the storage tank. After removing impurities through the filter, it is sent into the injection holes 3 of the compressor through the pipeline. The outlet pressure of the pump is usually set 20 - 30% higher than the pressure in the low-pressure compression chamber section of the compressor to ensure that the cooling medium can be smoothly injected into the compression chamber. The precision of the filter is usually selected as 1 / 3 of the diameter of the injection hole 3 to prevent impurities from blocking the injection hole 3.

[0047] The motor in the drive system is usually a variable-frequency motor, which can adjust the speed according to the load demand to improve the energy efficiency of the system. The motor and the male rotor are connected by a coupling or belt drive to ensure the smoothness of power transmission.

[0048] The control system monitors the temperature of each part of the compressor through a temperature sensor, monitors the inlet and outlet pressures of the compressor through a pressure sensor, and monitors the flow rate of the cooling medium through a flow sensor. The controller adjusts the speed of the motor and the flow rate of the cooling medium according to these parameters to ensure that the compression system operates in the best state.

[0049] In practical applications, the compression system can be used in various occasions such as air compression, refrigerant compression, and natural gas compression. Different application occasions may require adjusting the type and parameters of the cooling medium to adapt to different working conditions. For example, in air compression applications, lubricating oil is usually used as the cooling medium; in refrigerant compression applications, lubricating oil compatible with the refrigerant can be used as the cooling medium; in natural gas compression applications, special cooling media may be required to avoid reactions with natural gas.

[0050] Those of ordinary skill in the art can understand that the above-mentioned embodiments are specific implementation manners for implementing the present invention. In practical applications, various changes can be made to its form and details without departing from the spirit and scope of the present invention.

Claims

1. A compressor, characterized in that, It includes a housing, a compression chamber for installing a female rotor and a male rotor is formed inside the housing. The compression chamber sequentially includes a suction section, a low-pressure compression chamber section and a high-pressure compression chamber section along the axial direction of the rotor. A plurality of spray holes are provided on the housing, and all of the plurality of spray holes are located in the low-pressure compression chamber section. The spray holes are used for spraying a cooling medium into the compression chamber; the plurality of spray holes are distributed in a spiral line. The plurality of spray holes include a plurality of first spray holes, and the plurality of first spray holes are distributed in a first spiral line. The lead of the first spiral line is equal to the lead of the outer diameter of the male rotor tooth tip, and the helix angle of the first spiral line is equal to the helix angle of the male rotor.

2. The compressor according to claim 1, characterized in that, The plurality of spray holes include a plurality of second spray holes, and the plurality of second spray holes are distributed in a second spiral line. The lead of the second spiral line is equal to the lead of the outer diameter of the female rotor tooth tip, and the helix angle of the second spiral line is equal to the helix angle of the female rotor.

3. The compressor according to claim 1 or 2, characterized in that: The spray holes are atomizing spray holes, which are used for spraying a mist-like cooling medium into the compression chamber.

4. The compressor according to claim 3, characterized in that, The diameter range of the atomizing spray holes is 0.1 mm - 2 mm.

5. The compressor according to claim 2, wherein The starting angle of the first spiral line is determined by the following formula: ; The starting angle of the second spiral line is determined by the following formula: ; Wherein: is the starting angle of the first helical line, is the starting angle of the second helical line, is the intake angle of the male rotor, is the intake angle of the female rotor, is the number of teeth of the male rotor, is the number of teeth of the female rotor, is the tip radius of the male rotor, is the tip radius of the female rotor, is the diameter of the first injection hole, is the diameter of the second injection hole.

6. The compressor according to claim 1, wherein The number of the spray holes on the housing Satisfies: ; wherein, is the designed flow rate of the cooling medium, is the flow velocity of the cooling medium, is the diameter of the spray hole.

7. The compressor according to claim 1, characterized in that, The plurality of spray holes are spaced apart along the axial direction of the housing.

8. A compression system, characterized in that, It includes a compressor according to any one of claims 1-7.

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